|Publication number||US7109679 B2|
|Application number||US 10/797,787|
|Publication date||Sep 19, 2006|
|Filing date||Mar 9, 2004|
|Priority date||Mar 9, 2004|
|Also published as||CA2561131A1, CA2561131C, DE602004031464D1, EP1726087A1, EP1726087B1, EP1726087B8, US20050200328, WO2005096490A1|
|Publication number||10797787, 797787, US 7109679 B2, US 7109679B2, US-B2-7109679, US7109679 B2, US7109679B2|
|Inventors||Ralph D. Edson, M. Robert Mock|
|Original Assignee||Hr Textron, Inc.|
|Export Citation||BiBTeX, EndNote, RefMan|
|Patent Citations (31), Non-Patent Citations (4), Referenced by (21), Classifications (8), Legal Events (3)|
|External Links: USPTO, USPTO Assignment, Espacenet|
1. Field of the Invention
The present invention relates to oscillation damping in systems having electric motors for moving and positioning a load, such as a nose wheel of an airborne vehicle.
2. Description of the Related Art
For a long time, hydraulic systems have been used to move and position various components of aircraft and other vehicles and devices. One application of hydraulics has been in aircraft nose wheel steering (moving the aircraft's front wheel to a desired angular position). Nose wheels, like many other components, can be subject to shimmy or oscillation. These oscillations, particularly when at or near the resonant frequency, can cause damage to system components, reduce their life, weaken control and hinder accuracy. Accordingly, it is desirable to dampen vibrations of the load. Damping is often achieved when hydraulic power is used by forcing hydraulic fluid through an orifice.
It is desirable to use electric motors and in particular electromechanical actuators (EMAs) to move a nose wheel or other load. EMAs have no hydraulic fluid, so another form of damping is required. Unlike hydraulic actuators, EMAs intrinsically require a power train with a large gear ratio to deliver to the load the force (or torque) required by many applications, such as a steering actuator. It has been found that such a high gear ratio causes the system to be generally unresponsive to damping. In addition, conventional wisdom is that the requirement of power typically results in use of an electric motor with a stator diameter to rotor diameter ratio of equal to or about 2 to 1 or less.
One example of how damping has been attempted involves placing elastomeric damping elements in selected positions on the nose wheel assembly, such as in U.S. Pat. No. 6,247,687.
Oscillation damping with an electric motor such as in an EMA may be needed in nose wheel steering on an aircraft, such as a commercial aircraft, in shimmy damping of any vehicle steered with EMA or an electric motor, and any other electric motor or EMA actuation system for a load where load damping is used or required.
In one embodiment, vibration damping is provided for a system having a load driven by an electric motor, e.g., an EMA.
In a first preferred embodiment, oscillation damping is achieved using feedback in an active mode, where the actuator functions in a normal operation mode of the motor.
In a first version of this preferred embodiment, feedback is provided by measured force (or torque) transmitted between the load mass and actuator. A gear train or other mechanical advantage device may be connected between the actuator output and the load.
A variation of the first version is to measure acceleration of the load as a feedback signal, using e.g., an accelerometer.
A second version of the first embodiment of active mode damping uses the measurement of the motor's actual current as a feedback signal.
In certain active damping versions of the invention, a high pass filter may be used to pass on the high frequency portion of the feedback signals and filter out low frequency feedback.
In a second preferred embodiment, damping is achieved in an inactive (passive) mode of motor operation, e.g., where the electric motor is not receiving power (electrical drive signals). In this state, the motor is purposely shorted, e.g., using a switch. Load torques or forces, e.g. load shimmy, cause motor motion which produces short circuit motor currents. These currents produce reacting forces which provide actuator damping. Preferably, a resistance, e.g., a number of resistors, are in the short circuit to tailor the damping characteristics of the motor.
In accordance with a further aspect of the invention for the first and/or second embodiments, the inertia of the electric motor is substantially reduced in relation to typical motor inertia, by reducing the stator to rotor diameter ratio from a typical ratio of at or about 2:1 or less, to a substantially higher ratio than 2:1, e.g., from at or about 2.75:1, 3:1, 4:1, or 5:1 to as much as at or about 10:1, or more where possible. This low inertia motor is especially preferred for the current feedback version of the first embodiment of active damping, and also especially preferred for the second embodiment of passive damping.
A preferred embodiment of the invention includes moving a load using an EMA, and using the EMA to provide damping. The load is preferably a caster style wheel or fork mounted wheel for a vehicle, such as the front or nose wheel for a vehicle, such as an air vehicle, which is susceptible to shimmy.
In a first embodiment of the invention, a steering control system for a load, e.g., an aircraft nose wheel uses an electric motor. Specifically, as shown in
A controller 10 sends motor drive signals 12 to motor 2 so that load 4 is driven to a desired position. A position sensor (PS) 13 senses position of load 4, e.g., by sensing the position of part of the motor or the motor output shaft as may be done in a typical servo motor. As is also typical, the position signals are used as motor control signals 18 which provide position feedback to a controller 10. If load 4 moves from the desired position, controller 10 is programmed to send motor drive signals 12 as necessary to move load 4 back to the desired position. The motor drive signals typically are a voltage.
A transducer 14 measures load torque or force and sends feedback signals 16 back to controller 10 to drive motor 2 in a fashion that compensates for undesirable load oscillations, such as shimmy, and also maintains the desired position.
This system functions as a typical servo system which adjusts the motor drive signals 12 as needed to keep moving load 4 to the desired position as shimmy or disturbances occur. Electric motor 2 may be (or may be known as) a DC motor, a DC brushless motor, a synchronous motor, or the like, used as in an actuator.
Power train 6 may be a gear train. Controller 10 may be a microprocessor, computer, PLC, an analog electric control circuit or the like. Load 4 may be any movable object that experiences shimmy or otherwise may need load damping. One application where shimmy is a serious problem is in the nose wheel of an aircraft during takeoff, landing, and taxi. Accordingly, load 4 may be an aircraft nose wheel. In such an application, linkage 8 provides a connection from the output shaft of gear train 6 to the nose wheel, by any of various well known support structure to which the wheel axle is mounted, e.g., such as shown in U.S. Pat. No. 6,247,687. However, using the invention of the present inventors as described herein, elastomeric damping elements of U.S. Pat. No. 6,247,687 need not be used. Accordingly, linkage 8 may be relatively stiff, e.g., made of nonelastic, nondeformable members, e.g., of metal.
In an aircraft, because of the magnitude of the load, an electric motor would not normally be used. In accordance with the invention, to provide sufficient power to steer the nose wheel or control other such loads, the power train gear ratio is preferably high, e.g., at least 50 to 1, or more preferably at least 100 to 1, and most preferably 147 to 1.
In accordance with the first embodiment of the invention, a transducer 14 is used to measure force or torque transmitted between the electric motor 2 and the load mass, which would include load 4 and linkage 8. This transducer 14 would be positioned, e.g., at the output shaft of power train 6, so as to measure a force representative of that applied to the load. The feedback signals 16 (the measured force signals from transducer 14) would be fed back to controller 10. Similarly, the acceleration of the load mass may be measured using an accelerometer or the like as transducer 14, and feeding back the measured acceleration by signals 16 to controller 10 to achieve the same result.
The first embodiment may be varied by sensing and feeding back torque. In such case, transducer 14 senses torque.
Another embodiment is shown in
In accordance with one aspect of the invention, increase of the stator to rotor ratio above or substantially above at or about 2:1 is preferred, even though the efficiency and power to weight ratio are degraded for such a motor.
In the embodiment of
A high pass filter 16A may also be placed in or at controller 10 to filter feedback signals 16. The high pass filter removes or minimizes the influence of lower frequency feedback signals, passing frequencies at or near and above the frequencies of the undesirable oscillations or shimmy. In
In another embodiment of the invention, there is a passive or inactive damping of shimmy and other disturbances to the wheel or load movement. In the inactive mode, there is no feedback. To achieve inactive damping, the rotor diameter is reduced in relation to the typical stator to rotor diameter ratio of at or about 2:1. Reductions in rotor diameter relative to stator diameter increase the diameter ratio from at or about 3:1 to at or about 10:1 or even more, with at or about 3.5:1 being preferred for some systems. The reduction of relative rotor diameter dramatically reduces motor inertia and makes the motor more responsive to shimmy damping in the passive mode.
A passive energy dissipative element is also added to the system of
With reference to
With continued reference to
The effectiveness of the exemplary embodiments of active and passive damping is enhanced preferably in conjunction with use of a “low inertia” motor as motor 2 of
To test the preferred embodiments, various simulations were performed. Suitable commercially available simulation software may be licensed or purchased from various vendors, including The MathWorks, Inc. of Natick, Mass., sold under the name MATLABŪ simulation software such as SimPower Systems 3™, SIMULINKŪ and/or other simulation software.
To test the invention using active force or torque feedback, a mathematical simulation was set up as is well known in the art using the conditions set forth below.
The expected resonant frequency of load 4 of
Motor 2 was modeled as having 220V, a current limit of 18 amps operating at a nominal temperature of 77° F., and being a three phase Y wound motor. No velocity feedback was used. When load feedback and current feedback were used, a high pass filter of first order with a corner frequency of about 10 hertz was used.
The gear ratio (GR) was selected at 147:1, but it could be selected at almost any amount, e.g., equal to or about 50:1 or more, equal to or about 100:1 or more, or equal to or about 147:1 or more. A gear train efficiency was selected at about 71% to take frictional losses and the like into account.
Each angle θOUT and θCMD of the nose wheel is determined relative to twelve o'clock. In this simulation, an external sinusoidal force is acting on the nose wheel or system. The amplitude ratio of the actual nose wheel angle to the commanded angle is essentially or close to zero at one hertz, meaning the system outputs essentially the same wheel angle as that commanded. As one can see from the plot, as the position command frequency increases towards the resonant frequency of a shimmying wheel, the amplitude ratio increases dramatically. As the position command frequency approaches the shimmying nose wheel resonant frequency, the nose wheel becomes very dynamically compliant causing the actual angle to become quite large in comparison with the commanded angle. That is, at approximately 25 hertz the graph spikes up.
Although the invention has been described using specific terms, devices, and/or methods, such description is illustrative of the preferred embodiment(s) only. Changes may be made to the preferred embodiment(s) by those of ordinary skill in the art without departing from the scope of the present invention as set forth in the claims. Aspects of the preferred embodiment(s) generally may be interchanged in whole or in part.
|Cited Patent||Filing date||Publication date||Applicant||Title|
|US3569718 *||Jun 28, 1967||Mar 9, 1971||Telefunken Patent||Device for the fine adjustment of photomasks with respect to semiconductor elements|
|US3579071 *||Dec 23, 1969||May 18, 1971||Molekularelektronik||Electronic circuit arrangement for performing work steps in the production or testing of semiconductor means|
|US4267496||May 18, 1979||May 12, 1981||Ivanov Gely M||Device for damping oscillations|
|US4313364||Jun 4, 1979||Feb 2, 1982||Pneumo Corporation||Dual cylinder linear servo motor|
|US5184049||Jun 6, 1991||Feb 2, 1993||Sankyo Seiki Mfg. Co., Ltd.||Motor brake control circuit for reducing motor stopping time|
|US5545957||Jan 24, 1994||Aug 13, 1996||Hitachi, Ltd.||Motor speed controller for suppressing shaft torsion vibration|
|US5650704||Jun 29, 1995||Jul 22, 1997||Massachusetts Institute Of Technology||Elastic actuator for precise force control|
|US5726542 *||Apr 3, 1995||Mar 10, 1998||Nikon Corporation||Stage apparatus|
|US5757160 *||Dec 23, 1996||May 26, 1998||Svg Lithography Systems, Inc.||Moving interferometer wafer stage|
|US5886491||Aug 16, 1996||Mar 23, 1999||Mitsubishi Denki Kabushiki Kaisha||Position control unit for electric motor|
|US5894862||Jan 30, 1997||Apr 20, 1999||Vickers, Incorporated||Hydraulic damper|
|US5973467 *||Jun 18, 1998||Oct 26, 1999||Okuma Corporation||Velocity control device using servo motor|
|US6003481||Aug 22, 1997||Dec 21, 1999||Fev Motorentechnik Gmbh & Co. Kommanditgesellschaft||Electromagnetic actuator with impact damping|
|US6029959 *||Jan 8, 1999||Feb 29, 2000||Trw Inc.||Semi-active vibration isolator and fine positioning mount|
|US6034493||Feb 5, 1998||Mar 7, 2000||Fisher & Paykel Limited||Brushless DC motor control|
|US6122579 *||May 28, 1999||Sep 19, 2000||Delphi Technologies, Inc.||Electric power steering control with torque ripple and road disturbance damper|
|US6247687||Mar 29, 1999||Jun 19, 2001||Lord Corporation||Elastomer damper|
|US6279524||Feb 9, 2000||Aug 28, 2001||Fev Motorentechnik Gmbh||Electromagnetic actuator having a pneumatic dampening element|
|US6281643 *||Nov 18, 1997||Aug 28, 2001||Nikon Corporation||Stage apparatus|
|US6290038||Feb 22, 2000||Sep 18, 2001||Lord Corporation||Elastomer damper|
|US6373207||Jul 11, 2000||Apr 16, 2002||Kalish Inc.||Braking system for a DC motor|
|US6650079 *||Jun 1, 2001||Nov 18, 2003||Nikon Corporation||System and method to control planar motors|
|US6720746 *||Sep 6, 2002||Apr 13, 2004||Daimlerchrysler Ag||Method and regulating system for damping the torque oscillations of the drive train of an electrically driven road vehicle|
|US6832119 *||Sep 20, 2001||Dec 14, 2004||Ge Fanuc Automation North America, Inc.||Methods and systems for torque ripple compensation|
|US20020088678||Jan 5, 2001||Jul 11, 2002||Ruckman Christopher E.||Electromagnetic active vibration control system and electromagnetic actuator|
|DE10313604A1||Mar 26, 2003||Oct 9, 2003||Siemens Ag||Device for attenuating motor shaft vibrations allows coil components in a stator to be controlled separately by a frequency converter using a sensor signal regarding the shaft's radial position.|
|EP0658970A1||Dec 14, 1994||Jun 21, 1995||Fuji Electric Co., Ltd.||Motor vibration control device and method for matching a motor speed detected value with a motor speed reference value|
|EP0733578A2||Mar 25, 1996||Sep 25, 1996||Kone Oy||Device for emergency operation of an elevator motor|
|EP0845854A1||Aug 13, 1996||Jun 3, 1998||Kabushiki Kaisha Yaskawa Denki||Mechanical vibration detector and vibration damping controller|
|EP1120698A1||Sep 27, 1999||Aug 1, 2001||Kabushiki Kaisha Yaskawa Denki||Position controller|
|JP2001178182A||Title not available|
|1||David W. Robinson and Gill A. Pratt, Force Controllable Hydro-Elastic Actuator, MIT Leg Laboratory, 7 pages, Cambridge, MA.|
|2||Gill A. Pratt and Matthew M. Williamson, Series Elastic Acutators, MIT Artificial Intelligence Laboratory and Laboratory for Computer Science, pp. 399-406, Apr. 1995.|
|3||HR Textron, Airforce-Technology.com, Advanced EMA Controls, Precision Strike, WInning in the Air, 4 pages, printed on Dec. 10, 2003.|
|4||Michael Zinn, Oussama Khatib, Bernard Roth and J. Kinneth Salisbury, Actuation Methods For Human-Centered Robotics and Associated Control Challenges, 16 pages.|
|Citing Patent||Filing date||Publication date||Applicant||Title|
|US7431237||Aug 10, 2006||Oct 7, 2008||Hr Textron, Inc.||Guided projectile with power and control mechanism|
|US7520192||Nov 18, 2004||Apr 21, 2009||Hr Textron, Inc.||Reduced-friction drive screw assembly|
|US7584922 *||Dec 5, 2007||Sep 8, 2009||Diehl Bgt Defence Gmbh & Co. Kg||Spin-stabilized correctible-trajectory artillery shell|
|US7696459||Jun 12, 2007||Apr 13, 2010||Hr Textron, Inc.||Techniques for articulating a nose member of a guidable projectile|
|US7755012||Jan 10, 2007||Jul 13, 2010||Hr Textron, Inc.||Eccentric drive control actuation system|
|US7791007||Jun 21, 2007||Sep 7, 2010||Woodward Hrt, Inc.||Techniques for providing surface control to a guidable projectile|
|US7939984||Sep 23, 2008||May 10, 2011||Woodward Hrt, Inc.||Lamination having tapered tooth geometry which is suitable for use in electric motor|
|US8900325 *||Sep 24, 2013||Dec 2, 2014||Iwalk, Inc.||Hybrid terrain-adaptive lower-extremity systems|
|US8960386 *||Mar 31, 2009||Feb 24, 2015||Goodrich Actuation Systems Limited||Damping arrangement|
|US20060101930 *||Nov 18, 2004||May 18, 2006||Hr Textron Inc.||Reduced-friction drive screw assembly|
|US20080156939 *||Jan 3, 2007||Jul 3, 2008||Honeywell International, Inc.||Active pilot flight control stick system with passive electromagnetic feedback|
|US20080237391 *||Aug 10, 2006||Oct 2, 2008||Hr Textron, Inc.||Guided projectile with power and control mechanism|
|US20080302906 *||Dec 5, 2007||Dec 11, 2008||Diehl Bgt Defence Gmbh & Co. Kg||Spin-Stabilized Correctible-Trajectory Artillery Shell|
|US20080308671 *||Jun 12, 2007||Dec 18, 2008||Hr Textron, Inc.||Techniques for articulating a nose member of a guidable projectile|
|US20080315032 *||Jun 21, 2007||Dec 25, 2008||Hr Textron, Inc.||Techniques for providing surface control to a guidable projectile|
|US20090108702 *||Sep 23, 2008||Apr 30, 2009||Hr Textron, Inc.||Lamination having tapered tooth geometry which is suitable for use in electric motor|
|US20090242340 *||Mar 31, 2009||Oct 1, 2009||Goodrich Actuation Systems Limited||Damping Arrangement|
|US20100126786 *||Nov 25, 2008||May 27, 2010||Caterpillar Inc.||Electric drive inertia ratio for ttt|
|US20100147992 *||Jan 10, 2007||Jun 17, 2010||Hr Textron Inc.||Eccentric drive control actuation system|
|US20140081421 *||Sep 24, 2013||Mar 20, 2014||Iwalk, Inc.||Hybrid terrain-adaptive lower-extremity systems|
|EP2107004A2||Mar 27, 2009||Oct 7, 2009||Goodrich Actuation Systems Ltd.||Damping arrangement|
|U.S. Classification||318/611, 318/623|
|International Classification||H02P5/00, G05B5/01, G05B19/404|
|Cooperative Classification||G05B19/404, G05B2219/49054|
|Mar 9, 2004||AS||Assignment|
Owner name: HR TEXTRON, INC., CALIFORNIA
Free format text: ASSIGNMENT OF ASSIGNORS INTEREST;ASSIGNORS:EDSON, RALPH D.;MOCK, M. ROBERT;REEL/FRAME:015086/0280;SIGNING DATES FROM 20040302 TO 20040304
|Mar 19, 2010||FPAY||Fee payment|
Year of fee payment: 4
|Mar 19, 2014||FPAY||Fee payment|
Year of fee payment: 8